Repeating mechanical valve shutoff system



Aug. 3, 1943. c. BERGMAN EIFAL REPEATING MECHANICAL VALVE SHUT-OFF SYSTEM File d Feb. 2. 1949 3 Sheets-$heq 1 ATTORNEY Aug. 3, 1943. c. P. BERGMAN ETAL REPEATING MECHANICAL VALVE SHUT-OFF SYSTEM 3 Sheets-Sheet 2 Filed Feb. 2, 1940 6 ATTORNEY 1943- GP. BERGMAN ETAL 2,325,732

REPEATING MECHANICAL VALVE SHUT-OFF SYSTEM Filed Feb. 2, 1940 3 Sheets-Sheet 3 ATTORNEY barrels.

Patented Aug. 3, 1943 Charles P. Bergman. San Francisco, Calif., and Mead Cornell, Cleveland, Ohio, asslgnors, by

.mesne assignments Meter Company,

tion of Pennsylvania Pit to Pittsburgh Equitable tsburgh, Pa a corpora- Application male 2, 1940, Serial No. 316,888

3 Claims.

This invention relates to liquid measuring apparatus, and /more particularly to a repeating valve shut-off system, particularly for rapid measured filling of large containers, for example,

The primary object of our invention is to generally improve automatic valve shut-01f mechanisms, particularly for repeated shut-oi! at one quantity, as when filling uniform containers such as barrels. a a

A more particular object of our invention is to make it possible to use a valve at the nozzle end of a flexible hose, with all necessary starting controls centered at the nozzle, so that the operator may remain at the end of the hose, and insert the nozzle into the successive barrels, with no need to go to the trip register between filling operations.

Another object is to-eliminate the need for pump pressure delivery, the mechanism and valve being mechanical rather, than hydraulic, so that the barrels may readily be filled by gravity flow.

A further object of our invention is to provide an improved flexible motion-transmitting means between the starting lever at the valve, and the trip mechanism at the register.

Further objects center about the provision of an improved shut-oi! valve for the present purpose, and include making the internal valve body and the valve elements in smooth, streamlined form, with a nozzle discharge immediately below the valve, so as to avoid swirl, turbulence and foaming of the liquid; providing the valve body with a screen which further helps straighten out the liquid flow; making the valve and discharge nozzle as nearly as possible dripless, for which purpose the screen is located above the valve member; and making the ,valve member itself with a yieldable or gasket-like material (preferably Neoprene) held between upper and lower metal bodies, the said three parts of the valve member having the desired smooth, streamlined contour.

In accordance with other features and objects of the invention, thevalve is closed by spring pressure and is opened by cams rotated by a handle, and the cam action is taken through a in order to avoid side thrust on the valve rod. The valve is equipped with a dashpot which is so arranged asto slightly soften and time the closing of the valve when the handle is released by the trip mechanism. This helps insure accurately repeated delivery. The dashpot' is arranged-for spring movement in one direction, so that it need not be connected to the valve-opening handle and does not restrain opening of the valve,nor oppose the detent holding the valve open.

To the accomplishment of the foregoing and other objects which will hereinafter appear, our

invention consists in the repeating mechanical valve shut-off system elements and their relation one to the other,'as hereinafter are more particularly described in the specification and a sought to be defined in the claims. The specifipivoted arm held against longitudinal movement cation is accompanied by drawings in which:

Fig. l is a perspective view showing an automatic'valve shut-oi! system embodying features of our invention;

Fig. 2 is a partially sectioned side elevation of a metallic bellows used at the valve detent;

Fig. 3 is a partially sectioned elevation of a metallic bellows used at the register'trip mechanism; 1

Fig. 4 is a section taken in elevation through the valve used in the shut-oi! system;

Fig. 5 is a fragmentary section similar to Fig. 4, but showing the valve open;

Fig. 6 is a plan view of the valve with the arm and detent mechanism removed to better expos the parts therebeneath;

Fig. 7 is a plan view of the trip register mechanism with the cover removed, and may be considered as taken in the plane of the line 1-1 of Fig. 1;

Fig. 8 is a side elevation of a changeable gear plate looking in the plane of line 8-8 of Fig.

Fi 9 is a section taken in elevation in the plane of the line 8-9 of Fig. 7, withthe trip register mechanism removed from the meter body.

Referring to the drawings, and more particularly to Fig. 1, the shut-oi! system comprises a meter I! supported on a suitable pedestal I4 and supplied with liquid at the inlet It. The liquid is discharged at outlet l8 into a flexible pipe or hose 2!! of suitablelength. A trip register 22 is mounted on top of the meter body and is driven by the piston or driving element of the meter.

At the remote or free end of hose 20, a valve 24 is connected, the body of which includes a short downwardly directed nozzle 26 adapted to be freely inserted in the filling opening 28 of a barrel. The valve and nozzle may be moved The flow of liquid into the barrel iscontrolled' by means of a starting lever 40 which for this purpose, is pulled from the right-hand position shown, to the left-hand position 40', where it is held by suitable detent mechanism. A flexible motion-transmitting means extends between the valve 24 and the trip register 22. In the present case, this comprises a metallic bellows housed at 94 near the valve detent mechanism, and another metallic bellows housed at 36 near the trip mechanism, with a flexible tube 98 connected therebetween. By sealing a liquid in the bellows and tube assembly, movement applied to one bellows may be imparted from one bellows to the other. Thu the opening of the valve by lever 40 may be used to latch thetrip mechanism at register 22, and tripping at the register may later be used to release the valve detent and to cause closing of the valve. 1

Referring now to Figs. 4, and 6, it will be noted that the interior of valve bod 24 is given a smooth, streamlined shape leading into a short, straight, downwardly directed nozzle 26, and that the valve seat 42 does not appreciably change the desired streamlined shape. The valve member 44 is also given a smoothly tapered, streamlined configuration somewhat like a top or plumb-bob. As is best shown in Fig. 5, the valve member is made up of an upper metallic body 46, a lower metallic body 46, and a lamination of yieldable material or gasket-like member 50 therebetween. The latter may be squeezed between the upper and lower metallic bodies, as by means of nut 52 threadedly received on a threaded sleeve 54 formed integrally with and extendin upwardly over the lower part 48. The periphery of gasket 50 is made to conform to the desired tapered, streamlined shape of valve member 44. It bears against seat 42 primarily by reason of this taper. It may be made to project very slightly from the surface of the valve member, but this projection has been exaggerated in Fig. 5 in order to make the same visible. The gasket may be made of Neoprene. v

A valve rod 56 is fixedly secured to the valve member 44, as by means of a threaded connection. Reverting now to Fig. 4, it will be seen that valve rod 56 passes upwardly through a guide or bearing 58 of substantial length, and thence through packing which is compressed by a suitable threaded gland 60. The valve rod then passes through 2. preferably elliptical or elongated opening 62 in an arm 64 above which a pair of lock nuts 66 are secured. Elevation of arm 64 opens the valve. The valve is normally closed by means of a compression spring 68 housed within the valve body and surrounding the bearing 58, as is clearly shown in the drawings.

The valve body is made out of two main parts,

- the upper part I0 receiving the lower part I2 at a threaded connection 14. A wire mesh screen I6 is preferably clamped in position between the upper and lower parts I0 and I2, the function of this screen being to steady and to smoothen the flow of the liquid as it is changed from movement in a horizontal direction to movement in a vertical direction. It minimizes turbulence, and this is especially desirable when filling containers with a liquid having a tendency to foam. It

, should be particularly noted that the screen I6 from the tip of the nozzle, or when a screen such v as the screen I6 is disposed below the valve memher, for the screen itself tends to collect a considerable quantity of liquid in its mosh, which liquid later drips.

Referring now to Figs. 4 and 6, the starting lever or handle 40' is bifurcated at its lower end, it being divided into arms I8 which terminate in cams which preferably straddle the valve rod 56. The lower right-hand extremities of cam 80 may be connected by a suitable web or bridge 82, and all of these parts, that is, the handle 40, the arms I8, the cams 80 and the bridge 82, may be cast integrally. The arms I8 are pivotally mounted between stationary bearings 84 which project upwardly from and form a part of the upper valve body I0. While not essential, it is desirable that the cams 80 be pivoted on an axis intersecting the axis of valve rod 56. For this purpose the cams turn on studs or trunnions which terminate on each side of the valve rod 56. Specifically, the bearings 84 are threaded to receive screws 86 which are tightened into position and remain fixedl related to bearings 84. The inner ends 88 of screws 86 are turned smooth to act as pins freely received in cams 86.

One end of arm 64 overlies the cams 80 and acts as a cam follower. The other end 90 of arm 64 is received between the side walls 92 of the valve body. These side walls are designed to receive a part 94 projecting downwardly from and formed integrally with the bellows housing 34. When part 94 is fastened into position, it forms an effective part of the casing, and the end 90 of arm 64 is pivotally received between 'bears against the nuts 66 and raises the valve rod and thus opens the valve. No sideward thrust is applied to the valve rod because the end 90 of arm 64 abuts against the part 98 of the valve body. Moreover, the hole 62 through arm 64 is made over-sized and is preferably made elliptical with its longer axis extending lengthwise of the arm, so that there i clearance between the arm and the valve rod during operation of the handle 40.

When the handle is moved to its left-hand position, it is there held by suitable friction detent mechanism. In the present case the handle is provided with a spring-pressed ball I00 which is received in arecess I02 fixedly related to the valve body. Specifically, the recess I02 is an annular groove turned on the end of a rod I04 which is threadedly received in the part 94 of housing 34 and which is locked in position by a nut I06. The rod I04 may be turned somewhat when worn, thus presenting a new surface accuse spring. It will-be understood that the position of ball I relative to the stop groove I02 may be adjusted by sliding rod IIO longitudinally and then fixing its position by means of set screw H2. In this way the firmness of the detent action maybe adjusted.

when the starting handle 48 is swungto the left it bears against and presses a pin II8 inwardly. Referring now to Fig. 2, it will: be seen that pin H8 is secured to the movable righthand endof a metallic bellows I I8 of the Sylphon or similar type. The end to which pin II8 is secured, is sealed. The opposite end opens into a connection I20. the nipple I22 of which re-' ceives a flexible tube 38. The pin H8 is freely slidable in the end I24 of housing 34. The 0pposite end or head I28 of the housing is preferably supplied with the bellows, so that the two bellows and the connecting tube may form a sealed combination. In that case the housing is completed by simply assembling the head I26 with the shell 34, the latter being passed around the pin I I8 and bellows H8. The parts are secured together by screws I28.

Referring now to Fig. 8, it will be seen that a generally similar bellows I80 is provided within housing 38. In this case the lower end of the bellows is secured to the lower head I62, which in turn receives tube 38 by means of a nipple I64.

The upper end of bellows I34 is sealed, and carries a pin I38 which is slidable in a bearing I38 formed integrally with housing 38. The housing and the bottom head I32 are secured together by screws which are not visible in Fig. .3, but one of which may be seen at I40 in Figs. 1 and 9.

A suitable liquid is sealed within the bellows assembly and tube, and the resulting construction constitutes a flexible motion-transmitting means such that inward movement of pin II8 causes outward movement of pin I36,- and conversely, inward movement oi. pin I38 causes outward movement of pin II6. Thus, to shut the valve, the trip mechanism at the register forces pin I36 downwardly, thereby ejecting pin II6,

which in turn frees the detent action on handle 40 by simply forcibly dislodging the handle from the detent. The handle then swings over to the closing action slightly, but the closing action becomes a definite and timed action which helps obtain accurate repeat measurement, that is, the lag between tripping at the regi ter and closing at the valve is made a relatively fixed amount.

Referring now to Figs. '1 and 9, the trip register mechanism there shown is much like that disclosed in a co-pending application of Mead Cornell and Alexander R. Whittaker, Serial Number 260,210, filed March '1, 1939, and entitled "Repeating valve shut-oil system. However, in that case the trip mechanism was arranged for operation of a pilot valve of a hydraulic system, whereas in the present case the trigger action is applied directly to the pin I36 projecting upwardly from the bellows casing 36, the latter being attached to thehousing of the trip register, as shown in Figs. 7 and 9-of the drawings, as by means of the attaching flanges I62 and I64.

The drive from the meter is applied to shaft I66 (Fig. 9). This is connected through mitre gears I68, I80 to a sidewardly extending shaft I82 (Fig. 7 the latter carrying at its outer end a fixed or non-removable gear I64. This drives a worm shaft I66 through appropriate changeable gears. Worm I68 mounted on shaft I66 meshes with a subjacent worm gear I10 mounted on a forwardly extending shaft I12. This, in turn, drives shaft I14, but the drive is made indirect in order to accommodate a manual reset v mechanism which is subsequently described. Specifically, shaft I12 carries a gear I16 which meshes with an idle gear I18, which in turn meshes with a gear I80 carried on shaft I14.

Shaft I14 is geared to a cam shaft I82 by shaft 128 is given intermittent motion. The

transfer shaftalso carries a pinion I84 meshing with a gear I88 freely ,mtatable on the cam right-hand position shown in Figs. 1 and 4, the

valve being closed by its compression spring 88. Most of the closing movementof the handle is beyond its vertical position; so that the handle actually falls gravitationally.

In Fig. 4 it will be observed that the upper part of the valve body has a dashpot cylinder I42 formed integrally therewith. This cylinder is closed at the top by a cylinder head I44. A piston I48 is slidable in cylinder I42, and'is connected to arm 64 by means of apiston rod I48.

shaft. Gear I86-carries a cam shifter I98 while transfer shaft I88 carries a pin 208. When pin 200 and the cam shifter; I88 come into coincidence. the cam 202 {is moved axially against spring 204 into a position cooperative with a cam follower 208. This is preparatory to tripping of the valve, and as cam 202 is rotated by the cam shaft it raises the cam follower 208. .This trips the valve, as is later described.

The changeable gears are best shown in Fig. 8.

' Gear I64 is a. fixed gear permanently secured The piston I48 is urged upwardly by means of a spring I50. When starting handle 40 is moved to open the valve, the arm 64 is raised andleave's.

piston rod I48 behind. There is accordinglyno obstruction to very rapid opening of the valve,

. and no resulting wear or abuse of the dashpot mechanism. The valve remains open for a substantial period while the barrel is fllled, and during this time piston I48 is slowly raised by spring I60. '-It will be understood that the cylinder I42 maybe filled with oil, or more simply, with air,

as here shown. The damping action provided by the dashpotdepends upon the accuracy of the lit of piston I48 in cylinder I42, and need not be great.

When the valve is closed, the dashpot softens the closing impact oi the valve. It shows'up the to shaft I62. The changeable gears are an idler 2I0 and a driven gear 2I2, these being carried ona readily removable gear plate 2I4. Gear 2I2 is secured to a hub 2I6 having a square hole, and the outer or projecting and M8 of shaft I68 is squared to receive the gear. freely rotatable in plate 2I4, but is not removable therefrom. The idler or pinion 2" is freely r0.- tatable on but not removable from a stud 220 which is 'riveted to plate 2I4. Plate 2I4 is provided with a hole 222 which flts freely over the outermost end of shaft I82 (see Fig. '1). It is also provided with a slot 224 (Fig. 8) which flts s over the shank 228 of a thumb screw 228 (Fig.

9) The plate 2 I4 togetherwith the idler H0 and driven gear 2I2 is readily removed by removing the thumb screw 228, and thereupon moving the plate outwardly of! the shafts. Another The hub 2l6 is or after a greater flow.

plate with different gears: may be applied to,

change the trip quantity, all of the plates being interchangeable.

In each case the driven gear is so located relative to the hole 222 as to fit properly over the squareend 2I8 of shaft I66. The idler 2I0 is so selected as to mesh with the gears I64 and H2, for despite the fixed center-to-center distance of shafts I62 and I66, the size of gear 2I2 may differ on the different gear plates, the change being compensated by a different size or/and location of the idler. To prevent confusion, each plate is conspicuously marked with the number of gallons delivery it represents (see Fig. 8).

' The removable gear arrangement makes it readily possible to obtain a desired trip quantity by establishing the necessary gear ratio. Furthermore, the arrangement may be so designed that the number of teeth on the driven gear 2I2 corresponds numerically to the trip quantity or number of gallons to be supplied. Barrels range in size from fifty to fifty-five gallons. In the present apparatus, the gear 2I2 has fifty teeth for a fifty-gallon barrel, fifty-one teeth for a fifty-one gallon barrel, and so on. Ordinarily, the apparatus is supplied with six gear plates covering a range of from fifty to fifty-five gallons. However, a much wider range is available, and to fill special requirements the gear 2I2 may, for example, have only fourteen teeth, corresponding to the filling of small fourteen-gallon barrels.

The manner in which this result is obtained in the specific mechanism here disclosed, is as follows:

Referring to Figs. 7 and 9, the meter shaft I56 turns one rotation for one gallon of flow, (there being, of course, a reduction gear train between the meter piston and shaft I56, this being the so-called intermediate located near the top of the meter body). Shaft I62 also turns one revolution for one gallon. Fixed gear I64 has forty teeth. Assume driven gear 2I2 also has forty teeth, in which case shaft I66 and worm I66 turn one revolution for one gallon. The worm ratio is 10" to 1, and in the specific construction herein shown, the worm is a double worm, while the worm gear I10 has twenty teeth. The gears I16 and I are equal, hence shaft I14 turns once for ten gallons, and similarly the cam shaft I62 turns once for ten gallons. The mutilated or transfer gear I92 has ten teeth, while transfer pinion I 90 has eight teeth, thus producing one and one-quarter revolutions of the transfer shaft for one revolution of the cam shaft. Pinion I94 has eight teeth and gear I06 has twenty teeth, thus producing a reduction ratio of 2 to 1. The total reduction is, therefore, only 1 to 2. The reason a simple reduction of 1 to 2 is not used between'pinion I94 and gear I 96 is inorder to avoid premature tripping or contact between pin 200 and cam shifter I06. For these parts to engage requires two revolutions of the cam shifter, corresponding to five revolutions of the transfer shaft. This, in turn, requires four revolutions of the cam shaft, and inasmuch as each revolution corresponds to a flow of ten gallons, the arrangement will trip after a fiow of forty gallons.

For this result the driven gear 2| 2 on gear plate 2 was provided with forty teeth. If the driven gear 2I2 is given an increased number of teeth then the tripping point is reached later, Thus, with fifty teeth the apparatus will trip at fifty gallons, with fiftyoneteeth the apparatus will trip at fifty-one gallons, etc. Or, going in the other direction,-

with fifteen teeth the apparatus will trip at fifteen gallons.

In some cases the purchaser of the apparatus may require reset mechanism to manually restore the apparatus to zero whenever desired. This is of value, for example, when changing from one kind of oil to another, for in such case the meter and hose will be filled with the old oil. This may be discharged into a waste barrel or the like until the new oil comes through. For this purpose the discharge may be a matter of only ten or fifteen gallons. Without the reset mechanism the discharge of oil must be continued until an amount equal to a full barrel has been discharged, in order to bring the apparatus to zero preparatory to the filling of barrels with the new oil. By providing reset mechanism the extra waste is avoided.

Referring now to Figs. 7 and 9, knob 230 acts as a reset knob and is mounted on a shaft 232 which is both rotatable and axially reciprocable. The shaft is normally urged outwardly by a compression spring which may be housed at 234. Shaft 232 carries a large gear 236 which meshes with a pinion 238 (Fig. 7) carried on shaft I14. The idler gear-I18 is freely rotatable on shaft 232, but is axially movable therewith. Knob 230 cannot be rotated unless first pushed inwardly. If pushed inwardly the idler I 18 is disengaged from gear I80, and thereby frees the trip mechanism from the meter and from the totalizer, if a totalizer is used. Rotation of knob 230 rapidly spins the shaft I14 and consequently the trip mechanism. In this way, the trip mechanism may be turned to zero without any accompanyin: change of the meter and totalizer readin In order to determine the zero position, the cam shaft I82 is provided with an indicator wheel 2'40, said wheel having a series of arrows and a cross line 242 (Fig. 9) corresponding to zero. However, the indicator wheel 240 is not alone enough, because the cam shaft turns through four revolutions for the filling of one barrel. Another indicator wheel 244 is therefore provided, and this wheel is freely rotatable on the cam shaft, but is so geared to the transfer shaft as to turn only one revolution for four revolutions of the cam shaft. The wheel 244 is marked in fractions of a barrel, rather than in gallons, for the number of gallons differs in accordance with the size of the gear on the changeable gear plate.

The transfer mechanism for indicator wheel 244 includes a notched disc or mutilated gear 246 (Fig. 9) on wheel 240, this having four teeth. The transfer pinion 248 has eight teeth, and is, therefore, moved a half revolution. Transfer pinion 246 is secured to a pinion 250 which meshes in 2 to 1 ratio with a gear 252 secured to fraction wheel 244. In the specific case here shown the pinion 250 has twenty-four teeth and the gear 252 has forty-eight teeth. The total transfer reduction is, therefore, 4 to 1, the indicator wheel 240 turning four times for one complete revolution of the fraction wheel 244, which is as it should be. The two indicator wheels are exposed through a window 254, best shown in Fig. l. The knob 230 is simply rotated until the fraction wheel reads zero, and the cross line on the other wheel lines up with a suitabl pointer at the window 254.

Cam 202 is constantly rotating with cam shaft I 82'. For this purpose, a hub of the cam is splined or slidably keyed to shaft I82. The cam is normally moved away from the cam follower 206 by means of the compression spring 204, the parts then assuming the relation shown in the draws. .The trip element I88 forms a part of a cam shifter which is pivotally mounted at 266 between spaced arms secured to gear I86. The cam shifter is itself a forked member, the branches of which straddle the cam shaft I82. when the trip elements I88 and 200 come into engagement, the cam shifter is forced against the cam and moves it axially beneath the cam follower 206.

The trip elements I88 and 200 are adjusted to engage one another a little before the end of the run, causing cam 202 to slide'beneath the cam follower 206. The rise of the cam 202 then bears against the cam follower and raises it. The in-; termittent or Geneva type gearing between the shafts I82 and I88 make it possible for the cam to be shifted before the tripping point, so that the exact tripping point depends upon the shape of the cam.

Cam follower 206 is carried at the end of a cam follower arm 258 pivoted on a spindle 260. Arm 258 has a sidewardly projecting finger 262 which lies beneath hook 208, thus lifting the hook and disengaging tooth 264. Tooth 264 is formed on a disc 266 secured to a trigger shaft 268. Shaft 268 is normally urged in a counterclockwise direction (as viewed in Fig. 9) by means of a spiral ribbon spring 210, the inner end of the spring being secured to the shaft, and the outer end of the spring being connected to a stationary pin 212.

Outside the register casing the shaft 268 carries an arm 214, the end of which bears against the upper end of bellows pin I36 previously referred to. It will be evident that spring 210 normally urges arm 214 downwardly against the pin and so tends to compress the bellows. When the apparatus is started, and valve handle is pulled to open the valve, the pin I36 is forced upwardly, thus moving shaft 268 until trigger tooth 264 is engaged behind the hook 208. The detent at the valve is inadequate to restrain the powerful coiled trigger spring 210, but the spring is now restrained by latching of the trigger mechanism, and consequently the valve remains open even after the operator removes his hand from the valve lever. The bellows system is not under stress at this time, such as exists during the valve opening and valve closing operations. When the trigger mechanism is tripped, the .trigger spring 210 urges arm 214 downwardly, thereby depressing pin I36, and this in turn causes pin I I6 at the valve to dislodge the valve handle from the valve detent, whereupon the valve closes under the action of its own compression spring 68.

In the event of an emergency, the valve may be tripped closed by the operator standing at the valve, by simply pulling or biting the handle in the closing direction, thus dislodging it from its detent. The valve may also be tripped by an operator located at the meter, as by depressing the emergency trip button 216 which in turn causes rod 218 to bear against depending end 280 of cam follower arm 258, thus raising the cam follower and tripping the trigger mechanism of the register. e

The apparatus may be further refined by the use of a manually adjustable accuracy regulator which is interposed between the shaft I56 (Fig. 9) and the mitre gear I58 (Fig. 7). This accuracy regulator is preferably of the type disclosed in 5 theicircular part 282 of the register casing near the bottom thereof. It comprises-a tiltable ring 284 mounted on trunnions 288 and operating to oscillate an arm 288 connected to a pawl for intermittently moving a ratchet wheel 288 connected to a worm 282 meshing with a worm gear 284. The ring remains fixed in adjustment as determined by a manually operable knurled knob 286. A suitable scale and pointer as well as a locking screw, may be provided to fix the tilt or adjustment of the orbit ring 284.

Provision may also be made for temperature compensation. The temperature compensating mechanism may be of the type disclosed in the aforesaid co-pending application of Mead Gornell and Alexander R. Whittaker, Serial Number 260,270, and in the present case, is located in the neck 298 (Fig. 1) of the meter body. It comprises a mechanism much like that just described for accuracy regulation, but differing in having the orbit ring automatically fioatingly tilted by a temperature-responsive element such as a metallic bellows connected to a bulb or tube filled with a suitable liquid, and immersed in the fluid fiowing through the meter.

It is believed that the construction and operation, as well as the many advantages of our improved barrel filling mechanism. will be apparent from the foregoing detailed description thereof. The operator, after first setting the desired trip quantity by applying an appropriate gear plate to the side of the register, stands at the free end of the hose for operation of the valve. He inserts the nozzle part of the valve in a barrel opening and pulls the valve open by means of the handle. Liquid immediately fiows through the meter and valve into the barrel. This liquid may be under pump pressure, or may simply flow gravitationally. The operation of pulling the valve handle open, latches the trigger mechanism at the register. The fiow of liquid through the meter causes the meter to operate and to turn the register toward its trip point. when the trip point is reached, the trigger spring, is unlatched, and the resulting movement of the trigger mechanism is transmitted by means of the flexible bellows to release the valve handle, whereupon the valve closes. The operator then pulls the nozzle out of the barrel and inserts it in the next barrel, and again opens the valve. The setting at the trip register remains unchanged, and there is no need for the operator to move back and forth between the meter and the valve. His work can be carried out entirely at the valve. Thus one barrel after another can be rapidly and expeditiously filled. In the event of an emergency, theflow of liquid may be prematurely cut, off either at the valve or at the meter. In such case, the operation of the meter also stops, and will againcontinue only after the valve has been again opened.

The liquid flowing into the barrel is devoid of excessive swirl and turbulence, and has but little tendency to foam. When the valve is shut off, it is nearly dripless because the screen which helps straighten out the fiow of liquid, is located above the valve. The rate of closing of the valve is made uniform by the dashpot, but theconstruction of the dashpot is such as not to interfere with rapid opening of the valve. The valve is readily opened despite the use of a powerful valve spring, because the handle opens the valve through cams, thus providing a large amount of mechanical advantage. The construction of the Bergman PatentNo. 2,079,197. It is located in cam follower arm is such that there is no sideward thrust on 'the valve rod, and therefore no tendency to wear with consequent leakage at this point. i

It will be apparent that while we have shown and described our invention in a preferred form, many changes and modifications may be made in the structure disclosed without departing from the spirit of the invention as sought to be defined in the following claims.

We claim:

1. A valve comprising a valve chamber and valve seat, a valve member movable therein, a valve rod extending from said valve member, an oscillatable handle at the top of the valve, cams at each side of the valve rod rotated by said handle to lift the rod and open the valve, resilient means normally tending to close the valve, and friction detent means to hold the handle with the-valve open and fluid pressure operated means for freeing said handle from said friction detent to allow the valve to close.

2. A valve comprising a valve chamber and valve seat, a valve member movable therein, a

- valve rod extending from said valve, an oscillatable handle at the top of the valve, cams at each side of the valve rod moved by said handle, an arm overlying said cams and connected to said valve rod to raise the rod, resilient means normally tending to close the valve, means preventing longitudinal movement of the arm when the valve is opened in order to avoid sideward thrust on the valve rod, friction detent means to hold the handle when the valve is open and fluid pressure operated means for releasing said handle from said friction detent to allow the valve to close.

3. A valve comprising a valve chamber and valve seat, a valve member movable therein, a valve rod extending from said valve member, an oscillatable handle at the-top of the valve, cams at each side of the valve rod moved by said handle, an arm overlying said cams and connected to said valve rod to raise the rod, resilient means normally tending to close the valve, means preventing longitudinal movement of the arm when the valve is opened in order to avoid sideward thrust von the valve rod, friction detent means to hold the handle when the valve is open, a dashpot associated with said arm to soften and time the closing movement of the valve, said dashpot being so related to the arm as not to obstruct quick opening of the valve, and spring means inside the dashpot to cause the dashpot to follow the arm after the valve has been opened.

CHARLES P. BERGMAN. MEAD CORNELL.

or CORRECTION; A ust 19%.

of the aboie huhzb ei ed r; equ i z -ing correctioh as 'follbws; Page 5, firsteolunin, "line 75, 65. "eihbvia'" r e hd -slpws and that-the 5 11a Letters: Patent' should be reac l wijsh this -Brrectior; therein that the shine may. cbnfom to the' recerdbfthgca se 11d fihe'Pgtp-mt Office.

Signed and sealed this 'da a qfflflovmbier, A. 1p-. 19 45.-" 

